US9033029B2 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US9033029B2
US9033029B2 US13/358,699 US201213358699A US9033029B2 US 9033029 B2 US9033029 B2 US 9033029B2 US 201213358699 A US201213358699 A US 201213358699A US 9033029 B2 US9033029 B2 US 9033029B2
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Prior art keywords
refrigerant
holes
heat exchanger
header
partition
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US20130126140A1 (en
Inventor
Taegyun Park
Sehyeon Kim
Seungmo Jung
Eungyul Lee
Sanghoon Yoo
Naehyun Park
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LG Electronics Inc
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LG Electronics Inc
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Assigned to LG ELECTRONICS INC. reassignment LG ELECTRONICS INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: Lee, Eungyul, JUNG, Seungmo, KIM, Sehyeon, PARK, Naehyun, PARK, Taegyun, YOO, Sanghoon
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions

Definitions

  • This relates to a heat exchanger.
  • a heat exchanger may be a part of a heat exchange cycle.
  • the heat exchanger may serve as a condenser or evaporator to heat-exchange a refrigerant flowing therein with an external fluid.
  • Heat exchangers may be classified into a fin-and-tube type and a micro channel type according to a shape thereof.
  • the fin-and-tube type heat exchanger includes a plurality of fins and a tube having a circular shape or a somewhat circular shape passing through the fins.
  • the micro channel type heat exchanger includes a plurality of flat tubes through which a refrigerant flows and a fin disposed between the plurality of flat tubes.
  • a refrigerant flowing through the tubes is heat-exchanged with an external fluid, and the fin may increase a heat exchange area between the refrigerant flowing into the tubes or flat tubes and the external fluid.
  • FIG. 1 is a perspective view of a heat exchanger according to an embodiment as broadly described herein.
  • FIG. 2 is a sectional view taken along line I-I′ of FIG. 1 .
  • FIG. 3 is a sectional view taken along line II-II′ of FIG. 1 .
  • FIG. 4 is a perspective view of a header assembly of the heat exchanger shown in FIG. 1 .
  • FIG. 5 is a perspective view of a partition part of the heat exchanger shown in FIG. 1 .
  • FIG. 6 is a sectional view taken along line III-III′ of FIG. 4 .
  • FIG. 7 is a sectional view of a header according to another embodiment as broadly described herein.
  • Refrigerant flowing into a heat exchanger may be in a two-phase state. However, just before discharge from the heat exchanger, the refrigerant may be in a gaseous state or have a very high vapor quality. Thus, a flow rate of the refrigerant to be discharged from the heat exchanger may be relatively higher than that of the refrigerant introduced into the heat exchanger.
  • the refrigerant may be concentrated t an outlet side of the heat exchanger having a high-speed flow rate.
  • gravity may act on the refrigerant within the header to concentrate the refrigerant into the flat tubes disposed at a lower portion of the outlet side.
  • an amount of refrigerant flowing into one flat tube may be different from an amount of refrigerant flowing into another flat tube, thus deteriorating heat exchange efficiency.
  • a heat exchanger 10 may include headers 50 and 100 extending by a predetermined length in upward and downward directions, or a vertical direction, a plurality of flat tubes 20 coupled to the headers 50 and 100 to extend in a horizontal direction, or left and right directions, and a plurality of heatsink fins 30 arranged at a predetermined distance between the headers 50 and 100 and passing through the flat tubes 20 .
  • the headers 50 and 100 may be called “vertical headers” in that the headers 50 and 100 extend vertically.
  • the headers 50 and 100 include a first header 50 including a refrigerant inlet 51 through which refrigerant may be introduced into the heat exchanger 10 and a refrigerant outlet 55 through which refrigerant which has undergone heat-exchange in the heat exchanger 10 may be discharged, and a second header 100 spaced apart from the first header 50 .
  • First ends of the plurality of flat tubes 20 may be coupled to the first header 50
  • second ends of the plurality of flat tubes 20 may be coupled to the second header 100 .
  • a flow space for the refrigerant may be defined in each of the first and second headers 50 and 100 .
  • the refrigerant within the first or second header 50 or 100 may be introduced into the flat tubes 20 , and a flow direction of the refrigerant flowing into the flat tubes 20 may be converted in the first or second header 50 or 100 .
  • a flow direction of the refrigerant flowing in a left direction through the flat tubes 20 may be converted in the first header 50 to flow in a right direction.
  • a flow direction of the refrigerant flowing in the right direction through the flat tubes 20 may be converted in the second header 100 to flow in the left direction (see FIG. 3 ).
  • the first header 50 and/or the second header 100 may be referred to as “return headers”.
  • the refrigerant inlet 51 may be disposed at a lower portion of the first header 50 , and the refrigerant outlet 55 may be disposed at an upper portion of the first header 50 .
  • the refrigerant introduced into the refrigerant inlet 51 may flow in a direction opposite to that of gravity while circulating through the flat tubes 20 and then be discharged through the refrigerant outlet 55 . That is, the refrigerant may flow upward from the refrigerant inlet 51 toward the refrigerant outlet 55 .
  • the plurality of flat tubes 20 may be disposed between the first and second headers 50 and 100 , and may be spaced apart from each other in a vertical direction so as to form a vertical stack of flat tubes 20 .
  • Each of the flat tubes 20 may include a tube body 21 defining an outer appearance thereof and one or more partition ribs 22 defining a plurality of refrigerant passages 25 (i.e., micro channels) within the tube body 10 that allow refrigerant to uniformly flow into the plurality of refrigerant passages 25 .
  • Through holes 32 through which the plurality of flat tubes 20 pass may be formed in the fin 30 .
  • One or more baffles 58 for guiding the refrigerant so that the refrigerant flows along a zigzag pattern via the first header 50 , the flat tubes 20 , and the second header 100 may be provided in the first header 50 and/or the second header 100 .
  • the one or more baffles 58 may partition an inner space of the first and/or second header 50 or 100 into upper and lower portions.
  • a passage of the refrigerant flowing along the flat tubes 20 may form an S shape due to the baffle(s) 58 .
  • contact area and time between the refrigerant and air may increase to improve heat exchange efficiency.
  • the inner space of the first header 50 and/or the second header 100 may be partitioned into a plurality of spaces by the baffle(s) 58 .
  • Each of the partitioned spaces may form a space in which a refrigerant flow into the flat tubes 20 starts.
  • a partition device 150 for partitioning the inner space of the second header 100 in left and right directions and a blocking rib 158 disposed at a lower portion of the partition device 150 may be provided in the second header 100 .
  • the partition device 150 may be provided in, for example, the uppermost space of the spaces partitioned by the baffle(s) 58 .
  • the blocking rib 158 may extend across a lower portion of the left or right space partitioned by the partition part 150 .
  • FIG. 3 illustrates a state in which the lower portion of the left space is covered.
  • the partition part 150 may be provided at a height corresponding to that of the refrigerant outlet 55 , and in particular, at a height corresponding to those of the plurality of flat tubes 20 coupled to one side (left or right side) of the refrigerant outlet 55 .
  • the partition 150 may be provided adjacent to a set of passages that is closer to the refrigerant outlet 55 than the refrigerant inlet 51 .
  • the inlet 51 and outlet 55 are respectively provided at lower and upper ends of the first header 50 , with multiple baffles 58 in each of the first and second headers 50 and 100 forming multiple partitioned spaces therein.
  • the arrangement of the inlet 51 , outlet 55 , partition device 150 , blocking rib 158 , number and arrangement of baffles 58 may all be adjusted as necessary/appropriate for a particular application/environment.
  • the refrigerant introduced through the refrigerant inlet 51 flows into the plurality of flat tubes 10 in a right to left direction when viewed in FIG. 3 .
  • An upward flow of the refrigerant above a predetermined height may be restricted by the first baffle 58 provided in the first header 50 above the refrigerant inlet 51 .
  • the refrigerant passing through the flat tube 20 flows upward in the second header 100 , and then a flow direction of the refrigerant is converted to flow a left to right direction.
  • an upward flow of the refrigerant above a predetermined height may be restricted by the baffle 58 disposed in the second header 100 .
  • the refrigerant circulation process (left to right or right to left flow) may be repeatedly performed, as shown, for example, in FIG. 3 . As described above, the repetition of the refrigerant circulation process may be facilitated by the baffle(s) 58 . The refrigerant flow may progress upward toward the refrigerant outlet 55 , i.e., in a direction opposite to that of gravity.
  • the refrigerant passes through the partition part 150 to flow into the flat tubes 20 .
  • the refrigerant is introduced into the first header 50 and discharged to the outside of the heat exchanger 10 through the refrigerant outlet 55 .
  • the second header 100 may include a header body 110 defining a refrigerant flow space and a tube coupling plate 120 covering a front side of the header body 110 and coupled to the flat tubes 20 .
  • the header body 110 and the tube coupling plate 120 may be separate parts that are coupled together or may be integrally formed.
  • a plurality of coupling holes 125 may be formed in the tube coupling plate 120 .
  • the number of coupling holes 125 may correspond to that of the flat tubes 20 .
  • the plurality of coupling holes 125 may be vertically spaced apart from each other.
  • the plurality of coupling holes 125 may be spaced apart from each other at the same distance.
  • the partition device 150 for partitioning the flow space within the second header 100 may extend downward from an inner surface of an upper end of the header body 110 .
  • the partition device 150 may horizontally partition an upper space of the second header 100 .
  • the partition device 150 may extend substantially parallel to a flow direction of the refrigerant.
  • the partition device 150 includes a partition plate 151 having a plate shape and a plurality of holes 154 , 155 and 156 passing through the partition plate 151 and disposed along the flow direction of the refrigerant.
  • the partition plate 151 may function as a “blocking plate” which partitions a portion of the inner space of the second header 100 to prevent the refrigerant from being introduced all at once into a specific flat tube 20 .
  • the plurality of holes 154 , 155 and 156 may guide the refrigerant flowing through the partition device 150 so that the refrigerant flowing along one side of the partition plate 151 is uniformly distributed as it flows to the other side of the partition plate 151 .
  • the plurality of holes 154 , 155 and 156 may include a first hole 154 disposed at an uppermost end with respect to the flow direction of the refrigerant, a second hole 155 spaced apart from the first hole 154 in the flow direction of the refrigerant, and a third hole 156 spaced apart from the second hole 155 in the flow direction of the refrigerant.
  • the second hole 155 is disposed downstream from the first hole 154
  • the third hole 156 is disposed downstream from the second hole 155 .
  • the first hole 154 may be disposed at a lower end of the partition device 150
  • the second hole 155 may be disposed at an approximately central portion of the partition device 150
  • the third hole 156 may be disposed at an upper end of the partition device 150 .
  • a plurality of holes may be additionally disposed between the holes 154 , 155 and 156 .
  • multiple arrangements, combinations, shapes and/or sizes of holes may be appropriate.
  • the plurality of holes 154 , 155 and 156 may have sizes that different from each other.
  • the second hole 155 has a diameter “b” greater than a diameter “a” of the first hole 154
  • the third hole 156 has a diameter “c” greater than the diameter “b” of the second hole 155 .
  • the upstream hole may have a smaller overall size than that of downstream hole with respect to the flow direction of the refrigerant.
  • the plurality of holes may have gradually increasing sizes from the first hole 154 toward the third hole 156 .
  • the refrigerant introduced into the heat exchanger 10 may have a two-phase state.
  • the refrigerant may be evaporated while passing through the heat exchanger 10 to increase vapor quality.
  • the closer the refrigerant gets to the refrigerant outlet 55 the more the refrigerant reaches a gaseous state.
  • the refrigerant may be concentrated into at least one flat tube 20 of the plurality of flat tubes 20 before the refrigerant is discharged from the refrigerant outlet 55 .
  • the at least one flat tube 20 may be a lower flat tube 20 of the plurality of flat tubes 20 due to gravity.
  • a position of the first hole 154 may correspond to that of the lowest flat tube 20 of the plurality of flat tubes 20 covered by the partition device 150
  • a position of the third hole 156 may correspond to that of an uppermost flat tube 20 . That is to say, the first, second and third holes 154 , 155 and 156 may be sequentially disposed upward from a lower end of the partition plate 151 .
  • the refrigerant may be uniformly distributed into the second or third hole 155 or 156 having a size greater than that of the first hole 154 as well as the first hole 154 to pass through the holes 154 , 155 and 156 because the first hole 154 has the smallest size, rather than the majority of the refrigerant being concentrated at and directed into the lower flat tubes 20 .
  • the partition device 150 may include a top surface coupling device 152 defining a top surface of the partition plate 151 and coupled to an interior side of a top surface of the header body 110 , and a rib coupling device 153 defining a bottom surface of the partition plate 151 and coupled to the blocking rib 158 .
  • the partition device 150 extends downward from the top surface of the header body 100 by a predetermined length.
  • the blocking rib 158 is coupled to a lower end of the partition device 150 .
  • the blocking rib 158 extends forward from the lower end of the partition device 150 and is coupled to the tube coupling plate 120 .
  • the flow space of the refrigerant defined in an upper portion of the second header 100 is horizontally partitioned by the partition device 150 .
  • a first passage 170 through which the refrigerant flows toward the partition device 150 and a second passage 180 through which the refrigerant passing through the partition device 150 flows toward the flat tubes 20 are disposed in the partitioned flow space.
  • a passage inflow port 172 through which the refrigerant is introduced into the first passage 170 may be defined at a lower end of the first passage 170 by a space formed between the end of the blocking rib 158 and a corresponding surface of the header body 110 of the second header 100 .
  • the refrigerant introduced through the refrigerant inlet 51 flows upward while also performing heat exchange.
  • the refrigerant reaches an upper portion of the second header 100 , the refrigerant is introduced into the first passage 170 through the passage inflow port 172 .
  • the refrigerant may pass through the partition device 150 through the second or third hole 155 or 156 , each having a relatively larger size, as well as the nearest first hole 154 with respect to the flow direction of the refrigerant. That is, the refrigerant may be uniformly distributed as it passes through holes formed along the entire sectional area of the partition device 150 .
  • the refrigerant passing through the partition device 150 flows along the second passage 180 and then is introduced into the plurality of flat tubes 20 . Since the plurality of flat tubes 20 may be arranged to correspond to the partition device 150 , the refrigerant may be uniformly distributed into the plurality of flat tubes 20 .
  • refrigerant may be introduced into the second passage 180 through the passage inflow port 172 , the first passage 170 , and the partition device 150 .
  • each of the plurality of holes 154 , 155 and 156 shown in FIG. 5 has a substantially circular shape with a predetermined diameter
  • each of the plurality of holes 154 , 155 and 156 may have a different shape, such as, for example, a slit shape cut in a horizontal or a vertical direction, or other shape, size and/or orientation as appropriate.
  • a portion of the inner space of the header may be partitioned by the partition device shown in FIGS. 3-6
  • a separate tube instead of the partition device, may be provided to partition the refrigerant passage.
  • a second header 100 may include a plurality of partition devices 250 and 260 for partitioning an upper space of the second header 100 .
  • the plurality of partition devices 250 and 260 may include a first partition device 250 coupled to an end of a blocking rib 158 and a second partition device 260 spaced from the first partition device 250 , in the direction of a tube coupling plate 120 , and coupled to the blocking rib 158 .
  • a plurality of through holes through which refrigerant passes may be defined in the first partition device 250 .
  • the plurality of through holes may include, for example, a first hole 251 , a second hole 252 , and a third hole 253 which are disposed sequentially upward from a lower end to an upper end of the first partition device 250 .
  • a plurality of holes, in addition to the three through holes 251 , 252 and 253 shown in FIG. 7 may also be formed in the first partition device 250 .
  • the plurality of through holes 251 , 252 and 253 may have sizes gradually increasing from the first hole 251 toward the third hole 253 .
  • the first, second and third holes 251 , 252 and 253 may have substantially the same size.
  • Other arrangements, shapes, sizes and quantities of through holes may also be appropriate.
  • a plurality of through holes through which refrigerant passes are defined in the second partition device 260 .
  • the plurality of through holes may include, for example, a fourth hole 261 , a fifth hole 262 , and a sixth hole 263 which are disposed upward from a lower end to an upper end of the second partition device 260 .
  • a plurality of holes, in addition to the three through holes 261 , 262 and 263 shown in FIG. 7 may also be formed in the second partition device 160 .
  • the plurality of through holes 261 , 263 and 253 may have sizes gradually increasing from the forth hole 261 toward the sixth hole 263 .
  • the fourth, fifth and sixth holes 261 , 262 and 263 may have substantially the same size.
  • Other arrangements, shapes, sizes and quantities of through holes may also be appropriate.
  • An upper space of the second header 100 may be partitioned into a plurality of passages by the first and second partition devices 250 and 260 .
  • the plurality of passages may include a first passage 170 through which the refrigerant introduced into the upper portion of the second header 100 through a passage inflow port 172 flows toward the first partition device 250 , a second passage 180 through which the refrigerant passing through the second partition device 260 flows into flat tubes 20 , and a third passage 190 defined as a space between the first partition device 250 and the second partition device 260 to allow the refrigerant passing through the first partition device 250 to flow toward the second partition device 260 .
  • the through holes 251 , 252 and 253 of the first partition device 250 and the through holes 261 , 262 and 263 of the second partition device 260 may be disposed at different heights such that the holes of the second partition device 260 are somewhat offset from the holes of the first partition device 250 .
  • a position of the fourth hole 261 may be higher than that of the first hole 251
  • a position of the fifth hole 262 may be higher than that of the second hole 252
  • a position of the sixth hole 263 may be higher than that of the third hole 253 .
  • a lower end of the fourth hole 261 may be at a position corresponding to that of a central portion of the first hole 251
  • upper ends of the fifth and sixth holes 262 and 263 may be at positions corresponding to lower ends of the second and third holes 252 and 253 , respectively.
  • first, second and third holes 251 , 252 and 253 may be disposed at positions higher than those of the fourth, fifth and sixth holes 261 , 262 and 263 , respectively. Numerous other relative arrangements of the through holes formed in the first and second partition devices 250 and 260 may also be appropriate.
  • the through holes 251 , 252 and 253 of the first partition device 250 and the through holes 261 , 262 and 263 of the second partition device 260 may be positioned at different heights.
  • the flow of refrigerant passing through the first, second and third holes 251 , 252 and 253 into the fourth, fifth and sixth holes 261 , 262 and 263 may be somewhat impeded.
  • the flow rate of the refrigerant in the third passage 190 may be reduced, and kinetic energy of the refrigerant may be reduced.
  • Such an arrangement may prevent the refrigerant introduced into the first passage 170 through the passage inflow port 172 from being concentrated into the first hole 251 , and the refrigerant may flow into the second hole 252 or the third hole 253 due to an inertial force of the refrigerant.
  • a plurality of partition devices may be provided within the second header 100 , and the through holes defined in each of the partition devices may have different heights to reduce or regulate the flow rate of the refrigerant.
  • the refrigerant may be uniformly distributed into the upper through holes as well as the lower through holes of the plurality of through holes as it passes through the partition devices.
  • a partition device for guiding refrigerant flow may be provided in a header, and a plurality of through holes having different sizes may be defined in the partition device to allow refrigerant to be uniformly distributed.
  • the refrigerant may be easily drawn toward and through even the farther through holes.
  • a plurality of partition devices may be provided in the header to reduce or regulate a flow rate (or kinetic energy) between the plurality of partition devices and flow due to inertial force.
  • a flow rate or kinetic energy
  • Such an arrangement may prevent the refrigerant flow from being concentrated into a nearest through hole with respect to the flow direction of the refrigerant.
  • refrigerant may be uniformly distributed into the plurality of flat tubes to improve heat exchange efficiency between the refrigerant and the surrounding air.
  • any reference in this specification to “one embodiment,” “an embodiment,” “example embodiment,” etc. means that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment of the invention.
  • the appearances of such phrases in various places in the specification are not necessarily all referring to the same embodiment.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
US13/358,699 2011-11-18 2012-01-26 Heat exchanger Active 2033-01-19 US9033029B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR10-2011-0120898 2011-11-18
KR1020110120898A KR101372096B1 (ko) 2011-11-18 2011-11-18 열교환기

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US20130126140A1 US20130126140A1 (en) 2013-05-23
US9033029B2 true US9033029B2 (en) 2015-05-19

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US11236954B2 (en) * 2017-01-25 2022-02-01 Hitachi-Johnson Controls Air Conditioning, Inc. Heat exchanger and air-conditioner
US20220107146A1 (en) * 2019-08-01 2022-04-07 Hangzhou Sanhua Research Institute Co., Ltd. Heat exchanger and heat exchange system

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Cited By (5)

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Publication number Priority date Publication date Assignee Title
US10627139B2 (en) * 2014-11-11 2020-04-21 Trane International Inc. Suction duct and multiple suction ducts inside a shell of a flooded evaporator
US11365912B2 (en) 2014-11-11 2022-06-21 Trane International Inc. Suction duct and multiple suction ducts inside a shell of a flooded evaporator
US20160348982A1 (en) * 2015-06-01 2016-12-01 GM Global Technology Operations LLC Heat exchanger with flexible port elevation and mixing
US11236954B2 (en) * 2017-01-25 2022-02-01 Hitachi-Johnson Controls Air Conditioning, Inc. Heat exchanger and air-conditioner
US20220107146A1 (en) * 2019-08-01 2022-04-07 Hangzhou Sanhua Research Institute Co., Ltd. Heat exchanger and heat exchange system

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EP2597413B1 (fr) 2019-10-09
CN103123186A (zh) 2013-05-29
US20130126140A1 (en) 2013-05-23
JP5775226B2 (ja) 2015-09-09
CN103123186B (zh) 2015-08-12
KR20130055244A (ko) 2013-05-28
KR101372096B1 (ko) 2014-03-07
WO2013073842A1 (fr) 2013-05-23
EP2597413A1 (fr) 2013-05-29

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